WO2009065571A1 - Unité d'actionnement pour une boîte de vitesses à crabots et boîte de vitesses à crabots dotée de cette unité d'actionnement - Google Patents

Unité d'actionnement pour une boîte de vitesses à crabots et boîte de vitesses à crabots dotée de cette unité d'actionnement Download PDF

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Publication number
WO2009065571A1
WO2009065571A1 PCT/EP2008/009781 EP2008009781W WO2009065571A1 WO 2009065571 A1 WO2009065571 A1 WO 2009065571A1 EP 2008009781 W EP2008009781 W EP 2008009781W WO 2009065571 A1 WO2009065571 A1 WO 2009065571A1
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WO
WIPO (PCT)
Prior art keywords
shaft
positioning
elements
gear
actuator according
Prior art date
Application number
PCT/EP2008/009781
Other languages
German (de)
English (en)
Inventor
Wolfram Hasewend
Original Assignee
Magna Powertrain Ag & Co Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Magna Powertrain Ag & Co Kg filed Critical Magna Powertrain Ag & Co Kg
Priority to CN200880124941.9A priority Critical patent/CN101910686B/zh
Publication of WO2009065571A1 publication Critical patent/WO2009065571A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/304—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H2061/2838—Arrangements with single drive motor for selecting and shifting movements, i.e. one motor used for generating both movements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H2061/2869—Cam or crank gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/304—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force
    • F16H2063/3056—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by electrical or magnetic force using cam or crank gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/32—Electric motors actuators or related electrical control means therefor

Definitions

  • the present invention relates to an actuating unit for a dog transmission, in particular of a motor vehicle, with a shift fork, which is axially displaceable at least between a first position associated with a first gear stage of the doggear and a neutral position. Furthermore, the invention is directed to a claw transmission provided with such an actuating unit.
  • Claw transmission actuators are used on both automatic and manual transmissions.
  • powershift transmissions such as in dual-clutch transmissions or in automated manual transmissions.
  • each shift fork is assigned to a transmission shaft but non-rotatably arranged claw ring (shift sleeve), which is displaceable by the shift fork.
  • the claw ring is arranged in each case between on the transmission shaft rotatably but immovably arranged gear wheels (idler gears) and is pushed to connect a gear wheel with the transmission shaft via a ring gear of the corresponding gear wheel, whereby the gear wheel is positively connected to the transmission shaft and the respective gear wheel associated gear is inserted.
  • a position shaft is provided on the two positioning elements for the shift fork are axially displaceable but non-rotatably mounted, that the positioning each comprise a contact portion for temporary contact with the shift fork, that the position shaft is rotatable together with the positioning elements for setting predetermined different angular positions of the positioning elements and that each positioning element is associated with an actuating element, by means of which the positioning element is displaceable axially along the position shaft as a function of its set angular position.
  • a jaw gear with multiple sets of wheels for forming gear stages is described according to the invention, the arranged between the wheels sets claw rings (rotatably) for rotatably connecting rotatably mounted on a gear shaft gear wheels of the wheels with the transmission shaft and at least one inventively designed actuator unit for loading and unloading Has gear ratios.
  • two positioning elements are thus provided for the shift fork, by means of which an axial displacement of the shift fork occurs. wherein the positioning elements are in turn moved via actuators.
  • the positioning elements can be brought into different angular positions, wherein the displacement of the positioning elements by the actuating elements is dependent on the respectively set angular position of the positioning elements.
  • the invention thus takes place the engagement of a gear (gear stage) in a two-stage process, in which first the positioning are brought by turning in an angular position corresponding to the gear to be inserted and then in a second process step, the thus positioned positioning on the actuators to move the shift fork on the Position shaft are moved axially.
  • the shift fork is axially displaceable between the first position associated with the first gear stage of the doggear, a second position associated with a second gear stage of the doggear, and the neutral position, wherein the neutral position is located between the first and second positions.
  • a fully synchronized transmission can be realized.
  • each of the positioning elements is responsible for engaging one of the two gear ratios and for laying out the respective different gear ratio, as will be explained in more detail below. If the shift fork is displaceable only between the first position and the neutral position, then a semi-synchronized transmission can be realized, in which one of the positioning elements for the insertion and the other positioning element is responsible for the disengagement of the gear stage.
  • the invention can be applied to both semi-synchronized as well as fully synchronized gears or hybrids.
  • the positioning nieriata by the actuating elements relative to the shift fork so slidable that the contact sections come to rest against the shift fork.
  • a further displacement of the positioning of the shift fork is thereby taken to the desired target position, so that the desired shift of the shift fork takes place.
  • the positioning elements are displaced differently far as a function of the respectively set angular position. It is thereby achieved that by corresponding adjustment of the positioning elements into an angular position corresponding to the gear to be engaged, the positioning elements and thus also the shift fork corresponding to the gear to be engaged in the first position associated with the first gear, the neutral position or possibly the second gear second position is postponed.
  • the positioning elements are preferably a function of the respective angular position set by a predetermined simple switching path, the double switching path or not displaced.
  • a simple switching path in particular the distance between the first position of the shift fork and the neutral position is given, which optionally also corresponds in particular to the distance between the neutral position and the second position of the shift fork.
  • the Shifting the positioning by twice the switching path causes a shift of the shift fork in the first or possibly the second position, regardless of the respective starting position of the shift fork, which corresponds to an insertion of the first and second gear. Due to the possibility of ensuring, depending on the angular position of the positioning elements, that the positioning elements are not displaced, it is achieved that certain positioning elements have no influence on the shift fork assigned to them at certain angular positions, such that, for example, the displacement of the shift fork depends exclusively on the displacement the second of the shift fork assigned positioning depends.
  • the positioning elements comprise control sections which are arranged offset from one another in the axial direction, so-called insertion and disengagement sections.
  • control sections on which attack the actuators for moving the positioning are preferably arranged around the longitudinal axis of the positional shaft and, in particular, essentially concentric with the longitudinal axis of the positional shaft.
  • control sections are advantageously arranged in two, in particular mutually parallel, axially offset control planes of the respective positioning element, which form a Ausleg- control plane and a Einleg- control plane of the positioning.
  • the distance between the interpretation and the Einleg control plane corresponds advantageously to the simple switching path.
  • precisely one control section namely the insertion control section, is arranged in the insertion control plane, and in particular each control section is assigned to an angular position of the positioning element.
  • the tax deduction sections designed as circular or ring sectors.
  • the insertion control sections of different positioning elements are preferably offset in the circumferential direction relative to one another and, in particular, arranged without overlapping.
  • each insertion control section is assigned exactly one angular position and therefore exactly one predefined gear stage. If a positioning element is in an angular position in which the associated actuating element acts on the insertion control section during displacement, the positioning element is displaced by twice the switching path. This ensures that the shift fork is reliably moved to the position associated with the corresponding gear and the desired gear is securely engaged. Since the insertion control sections are arranged offset from one another in the circumferential direction, it is ensured at the same time that only one single insertion control section is acted upon by the actuation elements at each angular position of the positioning elements, so that engagement of a further gear step at the same time as the first gear step is excluded ,
  • At least one spring element is provided by which the positioning elements are biased away from one another in a direction or toward each other axially.
  • the actuating elements for moving the positioning elements in synchronism with each other are movable so that a predetermined distance between the Cyclically uniformly reduced actuators and again increased or increased and decreased again.
  • Each cycle can be a shift, that is, the engagement of a gear or the setting of the neutral position, each with simultaneous interpretation of any gear engaged, assigned.
  • the actuating elements are formed in particular parallel to the longitudinal axis of the position shaft against each other displaceable.
  • the actuating elements can be arranged, for example, on two parallel sliding rods.
  • Rotation / translation conversion unit coupled to the push rods by a predetermined rotational movement in an opposite, in particular cyclic translational movement of the push rods can be implemented.
  • a simple, for example, generated by an electric motor rotational movement in the desired cyclic, oppositely directed displacement movement of the actuators can be implemented.
  • the actuating elements are rotatable about a common axis of rotation, wherein the mutually facing sides of the actuating elements are at least partially formed as inclined to the axis of rotation oblique surfaces.
  • the actuating elements are advantageously arranged non-rotatably and axially non-rotatably on a common control shaft, wherein the control shaft can be rotated about its longitudinal axis.
  • the position shaft and / or optionally the rotation / translation s- conversion unit or the switching shaft are each operatively connected to a drive shaft of an electric motor. Both the adjustment of the desired angular position of the positioning as well as the respective displacement of the actuators is very easy to implement by using electric motors tax technology.
  • the same electric motor is provided for driving the position shaft and the rotation / translation s-conversion unit or the switching shaft, wherein the electric motor with the position shaft and the rotational
  • the positioning elements are arranged on two opposite sides in the axial direction of the neutral position of the shift fork.
  • the positioning elements can be arranged symmetrically to the neutral position, to ensure a uniform displacement of the shift fork.
  • a position detection unit in particular a sensor, is provided for detecting the current angular position of the positional shaft.
  • a position detection unit in particular a sensor, is provided for detecting the current angular position of the positional shaft.
  • the one-way clutches used unintentional rotation of the position shaft may occur, so that the current angular position of the position shaft and the positioning is detected via the position detection unit to ensure the correct angular position for the current gear to be engaged.
  • a control unit is provided, is ensured by the positioning of the positioning exclusively in the predetermined angular positions.
  • the control unit may preferably comprise a detent unit.
  • This embodiment provides a simultaneous actuation Prevention of adjacent control sections, which would lead to a faulty multiple insertion of aisles prevented.
  • a backstop may be provided for the position shaft or the positioning elements, by which an undesired reverse rotation of the position shaft and thus also a possible multiple insertion of gears is prevented.
  • Shifter forks provided, which are axially displaceable over correspondingly formed further positioning elements and actuating elements in each case two positions assigned to the further gear steps and a neutral position arranged between these positions.
  • multi-speed transmission can be provided, wherein usually each of a shift fork are assigned two different gear ratios.
  • two shift forks, for generating a six-speed shift, three shift forks, and so forth, are required for generating a four-speed shift.
  • Each shift fork is then assigned correspondingly described positioning elements and actuating elements.
  • each set angular position of the positioning elements in each case at most one of the positioning elements is displaceable by twice the switching path and thus forms an active positioning element. This ensures that even with just any number of adjustable gear ratios, only one gear can be automatically engaged at a time. Thus, a simultaneous insertion of two different gear ratios whose gear wheels are arranged on the same gear shaft, and a resulting destruction of the transmission reliably prevented.
  • the same shift fork as the active positioning and associated with the active positioning element opposite positioning in the set angular position is not displaced by its actuator. All other positioning elements, however, are displaceable in this angular position by the simple switching path. This ensures that when engaging a gear all other gears are designed automatically. Thus, a "fail-safe" function is achieved by the invention.
  • the drive shaft of the electric motor for driving a lubricant pump is operatively connected to a drive shaft of the lubricant pump. Since the electric motor used for the transmission is required only during the actual switching operation in order to bring the positioning elements in the desired angular position in a first step and in a second step on the actuators the desired gear, the electric motor during the remaining time be used to drive the lubricant pump.
  • a control element for driving a particular designed as a piston pump or as a diaphragm pump lubricant pump is provided on the position shaft.
  • the pump stroke can be effected as a function of the respective rotation of the position shaft, so that, for example, each time the positional shaft is rotated from one angular position to the next, a complete delivery cycle (suction and discharge of the lubricant) of the lubricant pump is passed through.
  • the use twistedg a diaphragm pump is particularly advantageous because it has a relatively small stroke, whereby a good dynamics and low noise is guaranteed.
  • diaphragm pumps are inexpensive to produce.
  • two or more actuating units designed according to the invention may be provided to form a double or multiple clutch transmission. Since, for example, in a dual-clutch transmission, the simultaneous insertion of two different gears on two different gear path may be useful so that, for example via a friction clutch seamless switching between the two inlaid gears is possible or, for example, when maneuvering the first and the reverse may be engaged, the implemented by the positioning elements switching logic be designed so that the simultaneous insertion of two different gears is prevented only for each separate sub-transmission.
  • FIG. 1 is a schematic representation of a partial transmission with claw circuit and an inventive actuating unit
  • FIG. 2 is a detail view of the actuating unit of FIG. 1, 3 shows a schematic representation of the control sections of the positioning elements designed according to the invention
  • FIG. 9 is a detail view of FIG. 1,
  • FIG. 10 is a side view of the view of FIG. 9,
  • Fig. 15 shows a further embodiment of the invention
  • FIG. 17 is a side view of the illustration of FIG. 16, Fig. 18 is a detail view from above of the embodiment according to
  • Fig. 20 shows another possible control of a lubricant pump
  • FIG. 21 is a side view of the illustration of FIG. 20th
  • Fig. 1 shows a part of a jaw gear, which is provided with an inventively designed actuator unit and otherwise formed in a known manner.
  • An input shaft 1 is connected via an input gear 2 with a Vorlegerad 3, which is connected to a countershaft 4 rotatably and axially immovably.
  • a countershaft 4 rotatably and axially immovably.
  • At the countershaft 4 are more Vorlegelig 5, 6, 7, 8 rotatably and axially immovably mounted, each with an axially on an output shaft 9 immovable, but rotatably mounted gear wheels 10, 11, 12, 13 are engaged and together with them
  • the claw rings 20, 21 are connected to shift forks 22, 23, whose ends are each formed as a shift sleeves 24, 25, via which the shift forks 22, 23 are rotatably and axially displaceably mounted on a position shaft 26.
  • Each shift fork 22, 23 are two laterally arranged by the shift sleeve 24, 25 positioning elements 27, 28, 29, 30 assigned, which are axially slidably mounted on the position shaft 26, however, non-rotatably attached.
  • a switching shaft 31 Parallel to the position shaft 26, a switching shaft 31 is provided, on which for each positioning element 27, 28, 29, 30 each have an actuating element 32, 33, 34, 35 rotationally fixed and axially immovable. Both on the position shaft 26 and on the switching shaft 31, a gear 36, 37 via a freewheel 68, 69 (see FIG. 10) are fixed, which are in engagement with a common screw 38, which is driven by an electric motor 39. By the gears 36, 37 and the screw 38 a fferradgetriebe is formed with high translation.
  • the freewheels 68, 69 of the gears 36, 37 are designed so that the position shaft 26 is rotated about its longitudinal axis 26 in a first direction of rotation only when the electric motor 39, while the switching shaft 31 only upon actuation of the electric motor 39 to their an axis of rotation 63 forming longitudinal axis 63 'rotated in the opposite direction of rotation. Since, due to the freewheels 68, 69, the positional shaft 26 or the selector shaft 31 may inadvertently rotate unintentionally in the direction not blocked by the respective freewheel 68, 69 can, sensors 108, 109 are provided, with which the respective angular position of the position shaft 26 and the shift shaft 31 can be detected.
  • any suitable position detection unit can be used with which the angular position of the two shafts can be detected.
  • the angular position can also be determined indirectly, for example by detecting the angular position of the positioning elements 27, 28, 29, 30 or the actuating elements 32, 33, 34, 35.
  • the switching shaft 31, the position shaft 26, the output shaft 9, the feed shaft 4 and the input shaft 1 are each arranged parallel to each other and rotatably supported by bearings 40.
  • the clamping ring 20 is shifted via the shift fork 22 on the output shaft 9 in the direction of the gear wheel 10 until the claw-shaped projections 14 engage in the holes 18 of the claw ring 20.
  • the gear 10 is rotatably connected to the output shaft 9, so that an input torque from the input shaft 1 is transmitted to the output shaft 9 in accordance with the translation of the Vorlegerades 5 and the gear wheel 10.
  • the gears 3, 5 and 7 can be inserted.
  • other known coupling elements for example, provided with external teeth, attached to the inner sides of the gear wheels switching rings may be provided, are pushed onto the respective shift sleeves.
  • the transmission described in Fig. 1 may have additional wheelsets to realize a larger number of gear ratios.
  • the transmission illustrated in FIG. 1 can also be a complete transmission or only a partial transmission, for example, of a dual-clutch transmission.
  • Fig. 2 the shift fork 22 is shown in its neutral position in which it is located together with the claw ring 20 in the middle between the gear wheels 10 and 11, so that neither the claw-shaped projections 14 nor the claw-shaped projections 15 in the holes 18th the claw ring 20 extend into it.
  • the gear wheels 10 and 11 are freely rotatable on the output shaft 9.
  • the positioning elements 27, 28 are supported by spring elements 41, 42 against side surfaces 43, 44 of the sliding sleeve 24 and are urged outwards due to the spring preload.
  • Fig. 2 while the positioning member 28 is shown in its outer end position, while the positioning member 27 is displaced against the spring force in the direction of the shift fork 22, as will be explained in more detail below.
  • the positioning elements 27, 28 are stepped in their radially outer regions, so that in the axial direction offset from each other control sections 45, 46, namely inner or Ausleg-control sections 45 and outer or Einleg-control sections 46 are formed.
  • the Ausleg-control sections 45 lie in a direction indicated by a dashed line inner or Ausleg- control plane 47, while the Einleg-control sections 46 are in a direction indicated by a dashed line outer or Einleg- control plane 48.
  • the lay-up and lay-in control planes 47, 48 are arranged parallel to one another and spaced apart from one another by the switching path s.
  • Control planes 48 each of the positioning elements 27, 28 divided into two part discs, namely an inner and a Operasteil 105 and an outer Einleg-part plate 106, each of the part discs 105, 106 has an axial thickness equal to the switching path s is.
  • the inner sides 49, 50 of the positioning elements 28, 27 pointing towards the shift fork 22 form abutment sections 51, 52 which come into abutment with the axial displacement of the positioning elements 27, 28 on the side surfaces 43, 44 of the shift sleeve 24, as is the case in the right part of FIG 2 is shown.
  • annular limit stops 53 are provided, in which, when a sliding apart of the positioning elements 27, 28 shoulders 54 come to rest, whereby a displacement of the positioning elements 27, 28 is prevented beyond their axial end positions.
  • the shoulders 54 are formed in bores 55 of the positioning elements 27, 28, through which the position shaft 26 is passed.
  • the bores 55 close radially outwardly parallel to the position shaft 26 extending grooves 56, 57, in which the ends are arranged displaceable by itself by the position shaft 26 extending radially therethrough securing pins 58, so that an axial displacement of the positioning elements 27, 28 while ensuring rotational resistance to the position shaft 26 is.
  • the actuators 32, 33 are formed as a cylinder with frontal inclined surfaces 64, 65, wherein the inclined surfaces 64, 65 face each other.
  • the inclined surfaces 64, 65 are arranged so that in each case the thinnest points in the axial direction and in the axial
  • each actuator 32, 33 has in the axial direction a length 2s, which corresponds to the double switching path s.
  • the inclined surfaces 64, 65 of the actuating elements 32, 33 form actuating surfaces for the positioning elements 27, 28.
  • the inclined surfaces 64, 65 come to the insertion control sections 46 to the plant in a further rotation, the positioning elements 27, 28 against the action of the spring elements 41, 42 are axially displaced, as indicated by in the right portion of Fig. 2 by a dash-dotted line 60 and further explained in more detail below.
  • each of the positioning elements 27, 28, 29, 30 in FIG. 3 is identified by its associated gear number (1 to 7 for gears 1 to 7 and R for reverse gear). Furthermore, the Partial disks 105, 106 of the control elements 27, 28, 29, 30 are each shown separated from one another, wherein in each case the outer or insertion part plate 106 is provided with an additional "a” and the inner or Ausleg part plate 105 with an addition "i” is. "Ia” thus characterizes, for example, the outer or insertion part plate 105 of the positioning element 27 required for inserting the first gear.
  • Each divider of the positioning elements 27, 28, 29, 30 is divided into ten annular sectors 59, which are separated from one another by distances 136, wherein the ring sectors 59 shown in FIG. 3 form the Ausleg representing, the Einleg- control sections 45, 46.
  • the ring sectors 59 (not shown in FIG. 3) form gaps 66.
  • Each outer or insertion disk 106 labeled "a" has exactly one outer or insertion control section 46 which is responsible for each positioning element 27, 28, 29 , 30 is arranged at a different angular position.
  • the ring sectors 59 thus define ten different angular positions for the position shaft 26 and the positioning elements 27, 28, 29, 30.
  • the angular orientation of the positioning elements 27, 28, 29, 30 shown in FIG. 3 in this case corresponds to the orientation in the case of positioning elements 27 fastened to the position shaft 26,
  • infeed control sections 46 which are shifted relative to each other about a ring sector 59 are assigned to successive gear steps. Circumferentially encircling the insertion control sections 46 on the individual positioning elements 27, 28,
  • Double clutch transmissions are used, in which one part of the transmission gear ratios 1, 3, 5 and 7 includes, while the second part transmission, the shift stages 2, reverse, 4 and 6 includes.
  • the partial disks 105, 106 of the actuating elements 27, 28, 29, 30 shown in the upper two lines in FIG. 3 are thus assigned to the partial transmission with a first positional shaft 26, whereas the partial disks 105, 106 of FIG Actuators 27 ', 28', 29 ', 30' are assigned to the second partial transmission with a second position shaft.
  • the shift fork 22 is in its neutral position, while the controls 27, 28 have already been brought by rotation of the position shaft 26 in an angular position, which is required for the insertion of the first gear.
  • the insertion control section 46 of the positioning element 28 is located in the direction of its actuating element 33, that is, in the region in which the actuating element 33 can basically come into operative engagement with the positioning element 28.
  • Shift fork 22 is shifted by the switching path s in their first position shown in Fig. 5.
  • the insertion of the third gear is done in an analogous manner by moving the positioning member 27 via the actuator 32 until the shift fork 22 is in a second position opposite the first position, in which the side surface 43 of the shift sleeve 24 on the inside 49 of the positioning 28 is present and this is in his in Fig. 6 left outside lying end position.
  • the position shaft 26 is first rotated in a first partial step so that the second gear associated, not shown positioning is brought into the angular position in which the insertion control portion of this positioning arranged facing the associated actuator. This is done in the same way as described for Fig. 4 for engaging the first gear.
  • both the positioning element 27 and the positioning element 28 are displaced in the direction of the shift fork 22. Since both positioning elements 27, 28 are displaced in opposite directions by the same switching path s, the shift sleeve 24 of the shift fork 22 ultimately lies in the middle between the end positions of the actuating elements 27, 28, so that the shift fork 22 in FIG is in its neutral position and thus the first gear was automatically designed simultaneously with the insertion of the second gear.
  • the positioning member 27 Since the shift fork 22 has been moved back by the positioning member 27 in the neutral position, the positioning member 27 is thus assigned to the design of the first gear, while the positioning member 28 is assigned according to the layout of the third gear.
  • the automatic laying out of gears when inserting a new gear can also be seen from the arrangement of the extension and insertion control sections 45, 46 of the respective positioning elements in FIG.
  • Each of the insertion control sections 46 is in each case arranged without overlapping with the insertion control sections 46 of the other positioning elements, that is, a gap 66 is provided on the other actuation elements respectively on the insertion part disc 106 at this angular position.
  • opposite positioning for example, the positioning element 27 of the third gear, which is opposite to the positioning element 28 of the first gear
  • opposite positioning also has the Ausleg-part plate 105 at the angular position to be set a gap 66. This is achieved in that, when the positioning element of the gear to be adjusted is displaced, the opposing positioning element is not displaced when the control shaft 31 is rotated (see FIG. 5).
  • combinations of simultaneously insertable gears are possible between two partial transmissions. So can For example, in the embodiment of FIG. 3 in the illustrated by the upper two rows part of the first gear and gearbox at the same time in the sub-transmission shown by the lower two rows of the reverse gear are inserted. Both gears can then be connected via a friction clutch to achieve greater variability, for example, when maneuvering.
  • FIGS. 4 to 8 switching tables are shown in each case in the upper left and right upper area, from which the possible switching operations can be seen.
  • the left vertical column which was labeled "Position was”
  • each of the three possible current gears, third gear, neutral position and first gear are listed.
  • the first horizontal line which is designated by “wheel position”
  • a position of the positioning element 27, 28 is marked with 0, at which the actuating element 32, 33 side facing (in Fig.
  • both partial disks 105, 106 have gaps 66, with I a position of the respective positioning element 27, 28, in which only the inner or Ausleg- part plate 105 in the lower part of an internal or Ausleg tax deduction section 45, and A denotes the position of the respective positioning element 27, 28, in which the outer or insertion control section 46 is arranged in the lower region of the positioning element 27, 28.
  • the values contained within the table respectively give the target gear, where 1, the first gear, 3, the third gear, N the neutral gear and 0 means "no effect", that is, no shift of the shift fork 22.
  • the position shaft 26 and the switching shaft 31 can be driven, for example, by an electric motor in each case.
  • FIGs. 9 and 10 the special embodiment of FIG. 1 in the neck shown, in which the position shaft 26 and the switching shaft 31 are driven by a single electric motor 39.
  • the screw spindle 38 is provided on the drive shaft 67 of the electric motor 39, via which both the gear 36 mounted on the position shaft 26 and the gear shaft 31 mounted on the gear 37 are drivable.
  • the two gears 36, 37 are mounted in each case via a freewheel 68, 69 on the position shaft 26 and the shift shaft 31, wherein the freewheels 68, 69 are formed so that the position shaft 26th only upon rotation of the drive shaft 67 in a first direction and the switching shaft 31 rotate only in rotation of the drive shaft 67 in the opposite direction.
  • the single motor 39 by changing the direction of rotation for engaging a gear first in the first step the positioning of the desired positioning and in the second step, when changing the direction of the motor 39, the engagement of the gear by a full rotation of the switching shaft 31 is possible.
  • atable actuating elements 32, 33, 34, 35 and sliding actuators 70, 71 may be provided, as shown in Fig. 11.
  • the switching shaft 31 is shown with the actuators 32, 33 in the upper part of Fig. 11.
  • Each of the slidable actuators 70, 71 is attached to a push rod 72, 73 which may, for example, have a semicircular cross-section and are arranged together in a guide tube 74, as can be seen in the cross section shown in FIG.
  • the actuating elements 70, 71 are guided in oblong holes 75, 76 and can each cyclically counter to the double switching path 2s. to be moved.
  • the movement of the displaceable actuating elements 70, 71 corresponds in its effect to the already described movement of the rotating actuating elements 32, 33, 34, 35.
  • a possible drive mechanism for the sliding actuators 70, 71 of Fig. 11 is shown.
  • the axially fixed in the housing-fixed guide tube 74 sliding rods 72, 73 are each provided with screwed bolts 77, 78, which in turn are axially displaceable in formed in the guide tube 74 slots 79, 80 slidably.
  • the free ends of the bolts 77, 78 are guided in a bearing of a screw drive 81, which forms a rotation / translation conversion unit 61.
  • the screw drive 81 consists of an inner part 82, which serves to receive a circumferential inclined bearing 83 and is connected via a clamping roller freewheel 84 with an outer part 85.
  • a gear 86 is formed, which meshes with the screw 38 and thus can be driven via the electric motor 39.
  • clamping roller freewheel 84 ensures that only in a first direction of rotation of the electric motor 39, the inner part 82 is rotated with, whereby the guided in the angular bearing 83 bolts 77, 78 are moved axially against each other cyclically.
  • the inner part 82 is decoupled from the outer part 85 via the clamping roller freewheel 84, so that no movement of the inner part 82 and thus no axial displacement of the bolts 77, 78 takes place.
  • the displaceable actuating elements 70, 71 from FIG. 11 as well as the drive unit from FIG. 12 are used.
  • a shift fork 22 ' is slidably mounted on the outside of the guide tube 74 via a shift sleeve 24', but mounted non-rotatably.
  • radially outwardly projecting lugs 87, 88 are formed, which contact with bearing portions 51 ', 52' of positioning elements 27 ', 28' when moving the positioning elements 27 ', 28' in contact ,
  • shifting the positioning elements 27 ', 28' ultimately displaces the shift fork 22 'into its desired position for engaging or disengaging gears.
  • the positioning elements 27 ', 28' are displaceably mounted on the position shaft 26, but non-rotatably mounted, wherein in this embodiment, a spring element 41 'is provided directly between the two positioning elements 27', 28 ', this in by delimiting elements 89, 90 defined outer end positions urges. Since the shift fork 22 'is not mounted between the positioning elements 27', 28 'on the position shaft 26, the shift sleeve 24' can be formed wider than in the first embodiment, whereby a better support against tilting forces is achieved.
  • the positioning elements 27 ', 28' are basically constructed like the positioning elements 27, 28 already described and are displaced differently far along the positional shaft 26 via the displaceable actuating elements 70, 71 depending on their respectively set angular position for engaging a desired gear.
  • the position shaft 26 and the guide tube 74 are arranged parallel to each other at such a distance that the free ends of the displaceable actuating elements 70, 71 come when moving to rest on a towards the guide tube 74 arranged inside or outside control portion 45, 46, such as it is shown in FIG. 13 by way of example for the outer control section 46 on the basis of the positioning element 27 'shown on the left.
  • a positioning element is set such that a gap 66 points in the direction of the guide tube 74, as is the case in the positioning element 28 'shown on the right in FIG. 13, the displaceable actuating element 70 passes under the positioning element 28' during displacement without causing a shift.
  • the displacement of the actuating elements 70, 71 takes place, as described for FIG. 12, via the screw drive 81, which is driven via the electric motor 39.
  • the gear 86 of the screw drive 81 is connected to a mounted on the outside of the position shaft 26 via a clamping roller freewheel 91 drive gear 92 for generating a translation into Quick.
  • the clamping roller freewheel 91 is designed so that only the rotational movement of the motor 39 is transmitted to the position shaft 26, which causes no displacement of the actuating elements 70, 71 due to the clamping roller freewheel 84 of the screw drive 81.
  • either the position shaft 26 for setting the desired angular position of the positioning elements 27 ', 28' can again be rotated via the direction of rotation of the electric motor 39 or, in the opposite direction of rotation of the electric motor 39, after setting the positioning elements 27 ', 28'.
  • the positioning elements 27 ', 28' are displaced via the actuating elements 71, 70, which in turn produces the desired te displacement of the shift fork 22 'has the consequence. In this way, therefore, the desired gear on or designed.
  • both the screw drive 81 and the position shaft 26 are driven by separate electric motors.
  • all other functions described for the first embodiment can also be realized correspondingly in the second exemplary embodiment according to FIG. 13 or the exemplary embodiments described below.
  • FIG. 14 This also applies to the third exemplary embodiment illustrated in FIG. 14. This differs from the exemplary embodiment according to FIG. 13 in that the guide tube 74 for the push rods 72, 73 and the displaceable actuating elements 70, 71 are arranged coaxially within a position shaft 26 'designed as a hollow shaft.
  • the position shaft 26 ' has elongated holes 93, 94, in which lugs 95, 96 of positioning elements 27 ", 28" are guided axially displaceable, so that the positioning elements 27 ", 28" relative to the position shaft 26' are non-rotatable.
  • the positioning elements 27 ", 28" are forced apart as in the exemplary embodiment according to FIG. 13 by a spring element 41 'and have radially inwardly projecting inner and outer control sections 45', 46 'or gaps 66', which in turn are configured in the manner of an annular sector and cooperate with the slidable actuators 70, 71 for displacing the positioning members 27 ", 28".
  • the guide tube 74 is analogous to the embodiment of FIG. 13 by a screw 81 'connected to the screw 38, wherein the screw drive 81' relative to the screw drive 81 described in Fig. 13 is only slightly modified with respect to the outer part 85.
  • the position shaft 26 ' is connected via an additional clamping roller freewheel 98 with an outer part 85' of the screw drive 81 ', so that upon rotation of the outer part 85' in a first direction, the position shaft 26 'and when turning in the opposite direction instead of the inside lying part 82 is rotated with.
  • FIG. 15 The exemplary embodiment illustrated in FIG. 15 is similar to the exemplary embodiment according to FIG. 13. Therefore, only the differences from FIG. 13 will be described in more detail below.
  • a shift fork 22 '" is displaceably mounted on the outside of the guide tube 74 via a shift sleeve 24'", but is mounted on the shift fork 22 "'opposite side of the shift sleeve 24'" radially outwardly projecting lugs 87 ', 88' While in the embodiment of FIG. 13, the outer regions of the lugs 87, 88 with abutment sections 51 ', 52' of the positioning elements 27 ', 28' in In the exemplary embodiment according to FIG.
  • positioning elements 27 ', 28'" arranged on the position shaft 26 do not project outside, but within the lugs 87 ', 88 'are arranged.
  • the positioning elements 27 "', 28'" have outer abutment sections 51 '", 52'" for this purpose and are urged towards each other by spring elements 41 "into their inner end positions, as shown in FIG. 15.
  • the positioning positioning elements 27 '', 28 '' of FIG. In contrast to the FIGS 2-8 and 13 and 14, the positioning positioning elements 27 '', 28 '' of FIG.
  • two actuating elements 70 ', 71' arranged on the push rods 72, 73 are provided which, in contrast to the embodiment according to FIG. 13, extend into the region between the positioning elements 27 "', 28 "'intervene and over the
  • Screw drive 81 cyclically moved apart and then be brought together again in the position shown in Fig. 15.
  • the actuating elements 70 ', 71' come into contact with one another when they move apart on the positioning elements 27 '", 28'", whereby they are displaced outwards.
  • the axially inner regions of the positioning elements 27 '", 28' form” insert control sections 46 ", which form extension control sections 45" during the axially outer regions.
  • the mode of operation of the embodiment shown in FIG. 15 completely corresponds to the mode of operation of the embodiment described with reference to FIG. 13.
  • the sensors 108, 109 shown in FIG. 1 may be provided, by which the respective correct angular position of the position shaft 26, 26 'and the shift shaft 31 can be detected. Furthermore, further controls may be provided to avoid, for example, in case of failure of the sensors 108, 109, a corresponding erroneous operation.
  • FIGS. 16 and 17 A corresponding control element is shown in FIGS. 16 and 17.
  • a control unit 111 comprising a ratchet wheel 110 is arranged to be unrotatable and axially immovable, which is provided with latching recesses 112 on its peripheral surface.
  • the latching recesses 112 are arranged distributed at the same angular intervals ⁇ as the ring sectors 59.
  • the angular positions of the latching recesses 12 correspond to the angular positions of the ring sectors 59.
  • the latching recesses 112 are separated from one another by ratchet teeth 113, which have a tapering shape in the axial direction, whereby deflecting surfaces 114 extending obliquely relative to each other and with respect to the longitudinal axis 62 of the positional shaft 26 are formed, as can be seen in particular from the detailed view in FIG ,
  • the angular positions of the ratchet teeth 113 coincide with the angular positions of the distances 136 between the ring sectors 59.
  • a bolt-shaped ramp element 115 is attached, which is displaceable together with the push rod 73.
  • an engagement element 116 is provided, which is designed as a latching and locking lever 117 and rotatably mounted about an axis of rotation 118.
  • the engagement member 116 is under spring bias that an engagement sabrisk 119 of the engaging member 116 is urged in the direction of the recesses 112 and engages at corresponding angular positions of the ratchet wheel 110 in a recess 112, as shown in FIG. 17 is indicated by a dash-dotted representation 120 of the engagement element 116.
  • engagement member 116 By engaging in the recess 112 engagement member 116 thus takes place locking the ratchet wheel 110 and thus a corresponding determination of the position shaft 26 exclusively in the predetermined different angular positions.
  • the arrangement of the latching recesses 112 and the ratchet teeth 113 thus ensures that upon engagement of the ratchet wheel 110, the actuators are each aligned centrally on a ring sector 59 and thus on exactly one control section. A simultaneous actuation of adjacent control sections is thus reliably prevented. Furthermore, an undesired turning back of the position shaft 26 against the direction of rotation shown by an arrow 135 caused by the electric motor 39, as is basically possible due to the freewheels 68, 69 used, is prevented.
  • the positional shaft 26 and thus also the ratchet wheel 110 are not located exactly in one of the predefined angular positions, but in an angular position, as shown for example in FIG. 17, when the push rod 73 is displaced the run-on element 115 runs on one The oblique deflecting surfaces 114, whereby the ratchet wheel 110 and thus the position shaft 26 and the associated positioning elements are also automatically moved to the correct angular position. A simultaneous actuation of two adjacent control sections is thus excluded. Since the positioning elements are connected to one another in a rotationally fixed manner via the common positional shaft 26, only one ratchet wheel 110 and a single casserole 115 are required for each positional shaft 26.
  • an oil sump which is deep enough to avoid immersion of the gears.
  • a demand-controllable electric oil pump can be used. Depending on your needs, this oil pump sprays oil onto the sprockets so that they do not run in an oil bath, which improves efficiency.
  • the electric motor 39 used for engaging the gears can be used simultaneously for driving an oil pump 99, as indicated in FIG. 19. Since the electric motor 39 is required for engaging and disengaging the gears only for a very short time, the torque available by the electric motor 39 during its inactivity can be used to actuate the oil pump 99 in the times between shifts.
  • the drive shaft 67 of the electric motor 39 is extended beyond the screw spindle 38 and connected to a drive shaft 107 of the oil pump 99, through which oil can be conveyed from an oil sump 100 to the gearwheels of the transmission.
  • the drive shaft 67 of the electric motor 39 does not have to be connected directly to the drive shaft 107 of the oil pump 99, respectively, but only a rotationally effective connection must be present. This can be done, for example, in the first case via the switching shaft 31 and the inner part 82 of the screw drive 81, 81 'and in the second case via the position shaft 26.
  • FIGS. 20 and 21 Another possible control of a lubricant pump 121 is shown in FIGS. 20 and 21.
  • a control element 122 in the form of a pump wheel 123 is arranged non-rotatably and axially immovably.
  • the peripheral surface 124 of the pumping wheel 123 is wave-shaped and is located on a coupling element 126 of a piston pump 127 designed as a roller 125.
  • the piston pump 127 comprises a piston 129, which is displaceably mounted in a cylinder 128 and which is provided by a spring 130 in the direction of the pump wheel 123. is tense.
  • the piston pump 127 is arranged in the oil sump 100, that sucked at an intake movement of the piston 129 according to an arrow 130 oil from the oil sump 100 and in a subsequent ejection movement of the piston 129 according to an arrow 131, the sucked oil is conveyed to the gears of the transmission ,
  • the wave-shaped circumferential surface 124 of the pumping wheel 123 comprises a number of wave crests 132 or troughs 133 corresponding respectively to the number of ring sectors 59 and similarly to the detent recesses 112 and the detent teeth 113 of FIG. 17, a detenting of the impeller 123 and thus also of the Ensure position shaft 26 and the associated positioning.
  • the angular positions of the wave troughs 133 coincide with the angular positions of the ring sectors 59, so that it is ensured that upon engagement of the roller 125 in a wave trough 133, the actuators are each aligned centrally on a ring sector 59 and thus to exactly one control section.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear-Shifting Mechanisms (AREA)

Abstract

La présente invention concerne une unité d'actionnement pour une boîte de vitesses à crabots, en particulier d'un véhicule automobile, comprenant une fourchette de boîte de vitesses qui peut être déplacée axialement au moins entre une première position associée à une première vitesse de la boîte de vitesses à crabots et une position neutre. Deux éléments de positionnement pour la fourchette de boîte de vitesses sont logés de manière à pouvoir se déplacer axialement, mais sans tourner, sur un arbre de positionnement. Les éléments de positionnement comportent respectivement une section d'appui destinée à les appuyer temporairement contre la fourchette de boîte de vitesses. L'arbre de positionnement peut tourner conjointement avec les éléments de positionnement pour régler les différentes positions angulaires prédéfinies des éléments de positionnement. A chaque élément de positionnement est associé un élément d'actionnement grâce auquel l'élément de positionnement peut se déplacer axialement le long de l'arbre de positionnement en fonction de sa position angulaire réglée. La présente invention concerne en outre une boîte de vitesses à crabots comprenant cette unité d'actionnement.
PCT/EP2008/009781 2007-11-20 2008-11-19 Unité d'actionnement pour une boîte de vitesses à crabots et boîte de vitesses à crabots dotée de cette unité d'actionnement WO2009065571A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN200880124941.9A CN101910686B (zh) 2007-11-20 2008-11-19 爪齿变速器的操作单元和具有这种操作单元的爪齿变速器

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DE102007055307.4 2007-11-20
DE200710055307 DE102007055307A1 (de) 2007-11-20 2007-11-20 Betätigungseinheit für ein Klauengetriebe und Klauengetriebe mit einer solchen Betätigungseinheit

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CN107044537A (zh) * 2016-02-05 2017-08-15 上海汽车集团股份有限公司 车辆及其变速箱、机械式操纵机构
CN106015561B (zh) * 2016-07-08 2018-07-06 新乡学院 一种变速箱机构
US10473542B2 (en) * 2016-12-22 2019-11-12 Eaton Cummins Automated Transmission Technologies, Llc System, method, and apparatus for operating a high efficiency, high output transmission
DE102019130357B4 (de) 2019-11-11 2022-03-10 Gkn Automotive Limited Aktuatoranordnung und Getriebeanordnung mit einer solchen Aktuatoranordnung

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EP1736678A2 (fr) * 2005-05-21 2006-12-27 Xtrac Limited Boîte de vitesses

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DE102007055307A1 (de) 2009-05-28
CN101910686B (zh) 2013-07-03

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